GB2277910A - Active wheel support system for vehicles - Google Patents

Active wheel support system for vehicles Download PDF

Info

Publication number
GB2277910A
GB2277910A GB9407747A GB9407747A GB2277910A GB 2277910 A GB2277910 A GB 2277910A GB 9407747 A GB9407747 A GB 9407747A GB 9407747 A GB9407747 A GB 9407747A GB 2277910 A GB2277910 A GB 2277910A
Authority
GB
United Kingdom
Prior art keywords
wheel
wheel support
mass
counter
support system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB9407747A
Other versions
GB9407747D0 (en
GB2277910B (en
Inventor
Michael Gipser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daimler Benz AG
Original Assignee
Daimler Benz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Benz AG filed Critical Daimler Benz AG
Publication of GB9407747D0 publication Critical patent/GB9407747D0/en
Publication of GB2277910A publication Critical patent/GB2277910A/en
Application granted granted Critical
Publication of GB2277910B publication Critical patent/GB2277910B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
    • F16F15/0275—Control of stiffness
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/16—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dynamic absorbers as main damping means, i.e. spring-mass system vibrating out of phase
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
    • B60G17/0155—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit pneumatic unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
    • B60G17/016—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
    • B60G17/0165—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input to an external condition, e.g. rough road surface, side wind
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/112—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on fluid springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/15—Fluid spring
    • B60G2202/152—Pneumatic spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/25—Dynamic damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B60G2202/41—Fluid actuator
    • B60G2202/412—Pneumatic actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/80—Exterior conditions
    • B60G2400/82—Ground surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/20—Spring action or springs

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Motorcycle And Bicycle Frame (AREA)

Abstract

The invention relates to an active wheel support system for vehicles having a scanning device 14 which registers surface unevenness in a roadway 2 and having active wheel support assemblies 3 which are controlled by means of the scanning device 14 in such a way that the wheels 4 are actively readjusted to the registered surface unevenness. The wheel support assemblies 3 are coupled in each case to counter-masses 5 which carry out movements opposite to the wheel movements relative to the vehicle body 1. The reaction forces exerted on the body 1 by the wheel movements are thus compensated by reaction forces directed in the opposite direction due to the simultaneous movement of the counter-masses 5. <IMAGE>

Description

2277910 1 Active wheel support system for vehicles The invention relates
to an active wheel support system for vehicles having a scanning device which registers surface unevenness in a roadway, and active wheel support assemblies controllable by said scanning device and with which the wheels are actively adjustable to the surface unevenness registered while the vehicle is travelling.
A system of this type is known, f or example, f rom DE-B 1,269,902. According to this publication, the roadway is scanned by means of a measuring beam, the deviation of the actual roadway compared to a virtual roadway being determined by the measuring beam, and the deviation measured being converted in direction and size to an adjustment of the wheel support assemblies so that the wheel movements no longer constitute a pure reaction to unevenness in the roadway, but rather a centrally precontrolled, intended avoidance or readjustment movement.
A basically identical system is the subject matter of DE-A 3,002,765, the emphasis in this latter publication being that, in such a wheel support system, the tyres can be pumped up to be significantly harder without reducing comfort. Accordingly, the rolling resistance of the wheels can be reduced considerably.
A further wheel support system is known from DE-A 4,037,223, in which active support assemblies are arranged, on the one hand, between the wheels (or the axles) and the vehicle body and, on the other hand, also between the wheels (or the axles) and absorption masses. The possibility is thus presented of damping the wheel movements, on the one hand, and the body movements, on the other hand, independently of one another. By means of the absorption masses which can be adjusted rapidly relative to the wheels, dynamic wheel load fluctuations and impairments of the driving safety and of the driving comfort, associated therewith, can be reduced considerably.
Practical tests have shown that the systems 2 represented at the beginning do not yet operate completely satisfactorily.
The present invention seeks to provide a wheel support system which is comparatively simple in terms of control and has considerably improved operating characteristics.
According to the present invention, there is provided an active wheel support system for vehicles having scanning device adapted to register surface unevenness in roadway, and active wheel support assemblies controllable by said scanning device and with which the wheels are actively adjustable to the surface unevenness registered while the vehicle is travelling, wherein each wheel is assigned a counter-mass which is coupled in terms of drive to the assigned wheel support assembly so as to move in the opposite direction to wheel movements relative to the vehicle body thereby to compensate reaction forces generated by active wheel movements.
The invention is based on the general concept of readjusting the wheels of a vehicle to the surface unevenness previously scanned and, during the readjustment movements of the wheels, to compensate inevitably occurring reaction forces between the wheels and the vehicle body by means of counter-masses guided in the opposite direction to the wheels. The vehicle body is thus kept f ree, to the greatest extent, from external forces caused by unevenness in the road.
In the case of support assemblies which react sufficiently rapidly, the wheels can be readjusted virtually exactly to the surface unevenness without the vehicle body being able to be accelerated simultaneously due to the readjustment movements of the wheels.
According to a preferred embodiment of the invention, provision may be 'made for the counter-mass to be smaller than the mass of the respectively assigned wheel (and the wheel guiding elements moving together with it) and for the drive coupling to operate with a path transmission 3 which compensates the difference in mass, such that the reaction f orces exerted on the body, on the one hand, by the wheel (and the parts connected thereto) and, on the other hand, by the counter-mass are mutually compensated.
If appropriate, the magnitude of the counter-mass and/or the size of the path transmission can be variable in order to be able to allow adaptation to dif f erent wheel masses.
The invention is described below by way of example with reference to the drawing in which the single figure shows a diagrammatic illustration of a wheel support assembly according to the invention.
According to the drawing, a scanning device 14 is arranged on the vehicle body 1 which is illustrated only diagrammatically, with which scanning device the profile and unevenness in a roadway 2 can be determined ahead of the vehicle in the travelling direction F.
The vehicle body 1 is connected via active wheel support assemblies 3 to the vehicle wheels 4, of which only a single wheel 4 is illustrated for reasons of simplicity.
The wheel support assemblies 3 are intended to be controlled as a function of the signals of the scanning device in such a way that each wheel 4 is readjusted as precisely as possible to the unevenness in the roadway 2.
In order to avoid ef f ects on the vehicle body 1 during the readjustment movements of the wheels 4, provision is made according to the invention f or each wheel 4 to be assigned a counter-mass 5 which is coupled in terms of drive to the respective wheel support assembly 3 in such a way that each wheel 4 as well as the associated counter-mass 5 carry out in-phase movements in opposite directions to one another relative to the vehicle body 1 in such a way that, during readjustment movements of the wheel 4, reaction f orces exerted on the vehicle body 1 by the wheel 4 are compensated by counter-forces of the counter-mass 5.
In this case, the mass of the wheel 4 and the mass of the counter-mass 5 can be of unequal sizes if the 4 movement strokes of the wheel and the counter-mass are correspondingly different, i.e. the product of the wheel mass and the stroke path of the wheel 4 must be (approximately) equal in size to the product of the countermass 5 and the stroke path of the counter-mass 5, the two products having opposite preceding signs due to the stroke paths of the wheel 4 and counter-mass 5 being directed opposite to one another.
A suitable wheel support assembly 3 is now illustrated diagrammatically in the drawing.
It comprises mainly a pneumatic cylinder 6 which is subdivided by two pistons 7 and 8 into three chambers 9 to 11. In the example illustrated, the outer chambers 9 and 11 are completely closed off towards the outside, whereas the middle chamber 10 can be pressurized by a pneumatic pressure medium by means of a pneumatic pressure source (not illustrated) or relieved from the pneumatic pressure via valves (not illustrated).
Depending on the magnitude of the pneumatic pressure in the middle chamber 10, the pistons 7 and 8 thus assume a more or less large distance from one another.
The pistons 7 and 8 are connected to the wheel 4 by means of a togglelike linkage arrangement 12, i.e. the wheel 4 carries out an upward stroke relative to the vehicle body 1 when the pistons 7 and 8 move away from one another; when the pistons 7 and 8 approach one another, the wheel 4 carries out a downward stroke relative to the vehicle body 1.
The counter-nass 5 is coupled in terms of drive to the pistons 7 and 8 by means of a toggle-like linkage 13 in basically the same manner as the wheel 4, but on the side of t L.he pneumatic cylinder 6 opposite the wheel 4. Accordingly, :Y the wheel 4 and the counter-mass 5 carry out lifting movements which are inevitably directed opposite one another relative to the vehicle body 1.
In the example illustrated, the masses of the wheel 4 and counter-mass 5 are intended to be different.
Accordingly, the toggle-like linkages 12 and 13 are dimensioned to be different so that the counter-mass 5, which is relatively small compared to the mass of the wheel 4, always carries out a stroke which is large compared to the wheel 4. If the wheel 4 is moved actively relative to the vehicle body by changing the pressure in the chamber 10, the counter-mass 5 carries out a corresponding movement in the opposite direction so that the dynamic movement forces exerted on the vehicle body by the wheel 4 and the countermass 5 are mutually compensated.
The active wheel movements caused by the active wheel support assembly 3 relative to the vehicle body 1 are thus incapable of leading to any (appreciable) acceleration of the vehicle body 1.
If the wheel 4 is readjusted exactly to the surface unevenness, essentially only a static supporting force acts as an external f orce on the vehicle body 1, while the dynamic f orces caused by the active wheel movements are compensated by opposing dynamic forces, caused by the counter-mass 5, and can only lead to internal forces.
If appropriate, the quantity of gas in the chambers 9 and 11 can also be varied in order to be able to vary the mean ground clearance of the vehicle or compensate f or a different payload of the vehicle body 1.
Differing from the design described above, the cylinder 6 may also be a hydropneumatic assembly which is subdivided by the pistons 7 and 8 into two outer pneumatic chambers 9 and 11 and one middle hydraulic chamber 10 which can be connected to a hydraulic pressure source or a relatively pressureless hydraulic reservoir.
If appropriate, all the chambers 9 to 11 can also be designed as hydraulic chambers, in which case, to adjust the wheel 4 relative to the vehicle body 1, each of the outer chambers 9 and 11 are connected to the hydraulic pressure source (or the reservoir) and the middle chamber 10 is connected to the reservoir (or the pressure source).
6

Claims (4)

Claims
1. An active wheel support system for vehicles having scanning device adapted to register surface unevenness in roadway, and active wheel support assemblies controllable by said scanning device and with which the wheels are actively adjustable to the surf ace unevenness registered while the vehicle is travelling, wherein each wheel is assigned a counter-mass which is coupled in terms of drive to the assigned wheel support assembly so as to move in the opposite direction to wheel movements relative to the vehicle body thereby to compensate reaction forces generated by active wheel movements.
2. An active wheel support system according to Claim 1, wherein the counter-mass is smaller than the mass of the respectively assigned wheel, and the drive coupling operates with a path transmission which compensates the difference in mass.
3. An active wheel support system according to Claim I or 2, wherein the counter-mass and/or the path transmission are variable for adaptation to different wheel masses.
4. An active wheel support system for vehicles substantially as described herein with reference to and as illustrated in the accompanying drawing.
GB9407747A 1993-05-03 1994-04-19 Active wheel support system for vehicles Expired - Fee Related GB2277910B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE4314516A DE4314516C1 (en) 1993-05-03 1993-05-03 Active wheel support for motor vehicle - has counter mass, drive coupled to wheel support of each wheel

Publications (3)

Publication Number Publication Date
GB9407747D0 GB9407747D0 (en) 1994-06-15
GB2277910A true GB2277910A (en) 1994-11-16
GB2277910B GB2277910B (en) 1996-07-31

Family

ID=6487006

Family Applications (1)

Application Number Title Priority Date Filing Date
GB9407747A Expired - Fee Related GB2277910B (en) 1993-05-03 1994-04-19 Active wheel support system for vehicles

Country Status (3)

Country Link
US (1) US5443282A (en)
DE (1) DE4314516C1 (en)
GB (1) GB2277910B (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2355239A (en) * 1999-10-15 2001-04-18 Meritor Heavy Vehicle Sys Ltd Predicting road profile

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19730414A1 (en) * 1997-07-16 1999-01-21 Opel Adam Ag Method to judge condition of roadway in advance
DE19755656C1 (en) * 1997-12-15 1999-08-26 Fkfs Forschungsinstitut Fuer K Vehicle suspension system
KR20010034768A (en) 1998-04-07 2001-04-25 피. 데니스 맥닐리 A suspension and a dynamic load-compensating fluid spring therefor
US6298791B1 (en) 1999-11-11 2001-10-09 Raytheon Company Lateral suspension assembly for a guided vehicle system
US6418856B2 (en) 1999-11-11 2002-07-16 Raytheon Company Passive steering assembly for a guided vehicle
US6308636B1 (en) 1999-11-11 2001-10-30 Raytheon Company In-vehicle switch mechanism
US6637561B1 (en) * 1999-11-11 2003-10-28 Raytheon Company Vehicle suspension system
DE19958178C1 (en) * 1999-12-02 2000-11-30 Daimler Chrysler Ag Spring shock absorber for automobile has coupling element between series carrier spring elements provided with damping mass attached via damping spring
US20040016361A1 (en) * 2002-04-26 2004-01-29 Martin Teichmann Level control for a rail-mounted vehicle
DE10360517B4 (en) * 2003-12-22 2006-08-31 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Device for secondary suspension of a car body in a rail vehicle with an active spring element
DE10360518B4 (en) 2003-12-22 2007-08-23 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Device for secondary suspension of a car body in a rail vehicle with a passive spring element
DE10360516C5 (en) * 2003-12-22 2010-12-16 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Device for secondary suspension of a car body in a rail vehicle with an active spring element
US7334801B2 (en) * 2005-01-28 2008-02-26 Hohmann Michael F Automated vehicle suspension system
CN100411895C (en) * 2005-09-15 2008-08-20 合肥工业大学 Steel cable-spring type automobile rear axle damper
US8285447B2 (en) * 2007-03-20 2012-10-09 Enpulz, L.L.C. Look ahead vehicle suspension system
WO2011127611A2 (en) 2010-04-16 2011-10-20 Ammann Schweiz Ag Arrangement for providing a pulsing compressive force
US10239377B2 (en) * 2014-07-18 2019-03-26 Piaggio & C. S.P.A. Vehicle with three or more wheels provided with an anti-roll stabiliser device and anti-roll control method of a vehicle having at least three wheels
RU2604250C2 (en) * 2015-03-27 2016-12-10 Федеральное государственное бюджетное образовательное учреждение высшего образования "Иркутский государственный университет путей сообщения" (ФГБОУ ВО ИрГУПС) Method and device for dynamic oscillations suppression

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1210712A (en) * 1968-03-29 1970-10-28 Daimler Benz Ag Improvements relating to methods and apparatus for controlling vehicle suspensions
US4518169A (en) * 1982-04-06 1985-05-21 Nissan Motor Company, Limited Automatic vehicle height-adjusting system
DE4037223A1 (en) * 1990-04-24 1991-10-31 Bosch Gmbh Robert VEHICLE SUPPORT SYSTEM

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE49228C (en) * H. OETTINGHAUS in Hagen i. W., Kuhlestr. 21 Elastic mounting of carriage and truck boxes
DE519996C (en) * 1927-02-12 1931-03-06 Ernst Kreissig Cushioning by a spring system
DE735806C (en) * 1936-05-12 1943-05-26 Georg Heinrich Schieferstein Vehicle wheel suspension, especially for motor vehicles
GB920586A (en) * 1960-09-21 1963-03-06 Bourcier Carbon Christian Improvements in or relating to pneumatic shock absorbers
DE1210712B (en) * 1961-04-17 1966-02-10 Eltreva Ag Opening device for parallel retractable and alternatively pivotable about a lateral axis wing of windows, doors or the like.
DE1269902B (en) * 1965-05-11 1968-06-06 Daimler Benz Ag Method and device for controlling a vehicle suspension, in particular in off-road vehicles
DE3002765A1 (en) * 1980-01-26 1981-07-30 Christoph Dipl.-Phys. 2283 Wenningstedt Schlobies Control system which adjusts position of vehicle wheels - measures distance between vehicle and ground and uses computer to make adjustments according to type of terrain
US4360087A (en) * 1980-05-27 1982-11-23 Mechanical Technology Incorporated Suspension and vibration isolation system for a linear reciprocating machine
SU947518A1 (en) * 1980-12-12 1982-07-30 Николаевский Ордена Трудового Красного Знамени Кораблестроительный Институт Им.Адмирала С.О.Макарова Vibration isolating suspension
US4483425A (en) * 1982-09-09 1984-11-20 North American Philips Corporation Vibration control system
SU1634864A1 (en) * 1988-06-21 1991-03-15 А.Д.Сепиашвили Vibration insulating device
DE3821386A1 (en) * 1988-06-24 1990-01-11 Nolde Sylvia Fruit-tea pastilles/dragées
DE3821368A1 (en) * 1988-06-24 1989-12-28 Audi Ag VIBRATION DAMPING AND VIBRATION COMPENSATING BEARING ARRANGEMENT
US4960290A (en) * 1989-05-10 1990-10-02 Bose Corporation Wheel assembly suspending
JPH03286040A (en) * 1990-03-31 1991-12-17 Toyo Umpanki Co Ltd Dynamic damper of vehicle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1210712A (en) * 1968-03-29 1970-10-28 Daimler Benz Ag Improvements relating to methods and apparatus for controlling vehicle suspensions
US4518169A (en) * 1982-04-06 1985-05-21 Nissan Motor Company, Limited Automatic vehicle height-adjusting system
DE4037223A1 (en) * 1990-04-24 1991-10-31 Bosch Gmbh Robert VEHICLE SUPPORT SYSTEM

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2355239A (en) * 1999-10-15 2001-04-18 Meritor Heavy Vehicle Sys Ltd Predicting road profile
GB2355239B (en) * 1999-10-15 2003-03-12 Meritor Heavy Vehicle Sys Ltd Method and system for predicting road profile

Also Published As

Publication number Publication date
DE4314516C1 (en) 1994-05-26
GB9407747D0 (en) 1994-06-15
US5443282A (en) 1995-08-22
GB2277910B (en) 1996-07-31

Similar Documents

Publication Publication Date Title
GB2277910A (en) Active wheel support system for vehicles
US5133575A (en) Vehicle with axle suspension device with gas spring suspension and control system therefor
US7631736B2 (en) Actuator for an active chassis of a motor vehicle
AU668826B2 (en) Parallelogram lift axle suspension system with a control for axle caster adjustment
US8608234B2 (en) Suspension device having active watt linkage
US7717438B2 (en) Chassis system for a motor vehicle and method for driving dynamics regulation
EP0185469A2 (en) Hydraulic stabilizing system for vehicle suspension arrangement
US6811166B2 (en) Clutched stabilizer bar
US10239377B2 (en) Vehicle with three or more wheels provided with an anti-roll stabiliser device and anti-roll control method of a vehicle having at least three wheels
AU5185401A (en) Self-steering, caster-adjustable suspension system
US6418856B2 (en) Passive steering assembly for a guided vehicle
CA2112671A1 (en) Vehicle suspension system
GB2309205A (en) Active roll control
US20070137913A1 (en) Active chassis for a motor vehicle
JPS61167729A (en) Spring cylinder for car, particularly, automobile
US5716067A (en) Mass spring system with roll/pitch stabilization for use in vehicles
US20040036244A1 (en) Hydraulic suspension system for a vehicle
JPH0211411A (en) Semi-working liquid pneumatic suspension system of automobile
US6739608B2 (en) Suspension system for a vehicle
US4589675A (en) Active suspension system
EP0975478A1 (en) Improvements to vehicle suspension systems
US8950757B2 (en) Device for the compensation of body movements of a motor vehicle
GB2473873A (en) Pneumatic secondary suspension for a rail vehicle bogie
EP0385618A1 (en) Vehicle suspension systems
US5608630A (en) Universal dynamic stabilizer

Legal Events

Date Code Title Description
732E Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977)
PCNP Patent ceased through non-payment of renewal fee

Effective date: 20020419